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United States Patent |
5,125,807
|
Kohler
,   et al.
|
June 30, 1992
|
Fuel injection device
Abstract
A fuel injection device for diesel engines, having at least one pump
plunger (4), which is sealingly guided in a plunger bushing (5) and forms,
together with said plunger bushing (5), a high-pressure space (11) that is
connected to a low-pressure space (13) by means of a control element
during the downward motion of the fuel pump plunger, said high-pressure
space (11) being placed in free flow communication with an injection valve
(49) via an injection line 48. The use of a continuously open flow
connection between the high-pressure space 11 and the injection valve 49
minimizes dead space thereby permitting development of high injection
pressures.
Inventors:
|
Kohler; Wolfgang (Cologne, DE);
Rizk; Reda (Cologne, DE);
Michels; Hans-Gottfried (Erftstadt, DE)
|
Assignee:
|
Kloeckner-Humboldt-Deutz AG (Cologne, DE)
|
Appl. No.:
|
502765 |
Filed:
|
April 2, 1990 |
Foreign Application Priority Data
Current U.S. Class: |
417/490; 123/458; 123/506; 251/129.16; 417/440 |
Intern'l Class: |
F04B 039/10 |
Field of Search: |
417/440,490,415,307
123/506,458,500
137/454.2
251/50,129.16,367
|
References Cited
U.S. Patent Documents
2700397 | Jan., 1955 | Compton | 417/440.
|
3701366 | Oct., 1972 | Tirelli et al. | 251/50.
|
3779225 | Dec., 1973 | Watson et al. | 123/506.
|
4445484 | May., 1984 | Marion | 123/506.
|
4616675 | Oct., 1986 | Amrhein | 251/50.
|
4619239 | Oct., 1986 | Wallenfang | 123/506.
|
4785787 | Nov., 1988 | Riszk et al. | 123/506.
|
4840162 | Jun., 1989 | Brunel | 123/506.
|
4971116 | Nov., 1990 | Suzuki et al. | 251/129.
|
4988967 | Jan., 1991 | Miller et al. | 251/129.
|
Primary Examiner: Bertsch; Richard A.
Assistant Examiner: Kocharov; Michael I.
Attorney, Agent or Firm: Schwab; Charles L.
Claims
The embodiments of the invention in which an exclusive property or
privilege is claimed are defined as follows:
1. A fuel injection device for diesel engines, comprising:
a fuel injection pump having
a one piece plunger bushing (5), including
a plunger bore with a first end which is open for receiving a plunger and a
second end,
a high pressure hole (12) in said plunger bushing (5) at said second end of
said bore, said second end of said bore being closed except for said high
pressure hole,
a high pressure space (11) at said second end of said plunger bore, and
wall means in said plunger bushing defining a stepped diameter bore, said
stepped diameter bore extending transverse to and intersecting said high
pressure hole closely adjacent to said high pressure space,
a low pressure space (13) connected to said plunger bore at a substantial
distance from said second end,
a pump plunger (4) reciprocatably mounted in said plunger bore,
a control valve bushing (17) having stepped diameter exterior surfaces in
complimentary fitted relation with said stepped diameter bore in said
plunger bushing, said control valve bushing having a stepped diameter
interior bore including a large diameter portion and a small diameter
portion and an axially facing sealing surface between said portions,
a stepped diameter control valve body (22) having a large diameter portion
and a small diameter portion in axial sliding engagement, respectively,
with said stepped diameter interior bore of said control valve bushing and
a control valve seat formed between said stepped diameter portions in
axially confronting relation to said sealing surface, said control valve
body being axially shiftable between a closed position in which said seat
is in sealing engagement with said sealing surface and an open position in
which said high pressure space is connected with said low pressure space,
a return passage (15) interconnecting said small diameter portion of said
stepped diameter bore with said low-pressure space (13),
a spring operatively interposed between said control valve bushing (17) and
control valve body (22) resiliently biasing the latter to its closed
position wherein said seat engages said sealing surface,
an injection valve (49) operable to inject fuel into an engine cylinder,
a high-pressure fuel line (48) connecting said high pressure hole (12) with
said injection valve (49),
a liquid-filled damping space (33) at one axial end of said control valve
bushing (17),
an anchor polate (30) secured to an axial end of said control valve body
(22) and disposed within said damping space (33),
a choke hole (37) connecting said damping space (33) in free flow
communication with said return passage (15),
a venting line (39) connected to the highest point of said damping space
(33),
a pressurizing valve (40) connected to said venting line (39) having a
relief pressure less than the pressure in said low-pressure space (13),
and
an electromagnetic actuating device operatively associated with said
control valve body and selectively operative upon actuation to move said
valve body to its open position in opposition to said spring,
said anchor plate and damping space, valve body, valve bushing, spring and
choke hole being proportioned and arranged to effect a recoilless seating
of said valve body seat on said sealing surface.
2. A fuel injection device for diesel engines, comprising:
a fuel injection pump having
a one piece plunger bushing (5), including
a plunger bore with a first end which is open for receiving a plunger and a
second end,
a high pressure hole (12) in said plunger bushing (5) at said second end of
said bore, said second end of said bore being closed except for said high
pressure hole,
a high pressure space (11) at said second end of said plunger bore, and
wall means in said plunger bushing defining a stepped diameter bore, said
stepped diameter bore extending transverse to and intersecting said high
pressure hole closely adjacent to said high pressure space;
a low pressure space (13) connected to said plunger bore at a substantial
distance from said second end,
a pump plunger (4) reciprocatably mounted in said plunger bore;
a control valve bushing (17) having stepped diameter exterior surfaces in
complimentary fitted relation with said stepped diameter bore in said
plunger bushing, said control valve bushing having a stepped diameter
interior bore including a large diameter portion and a small diameter
portion and an axially facing sealing surface between said portions,
a stepped diameter control valve body (22) having a large diameter portion
and a small diameter portion in axial sliding engagement, respectively,
with said stepped diameter interior bore of said control valve bushing and
a control valve seat formed between said stepped diameter portions in
axially confronting relation to said sealing surface; said control valve
body being axially shiftable between a closed position in which said seat
is in sealing engagement with said sealing surface and an open position in
which said high pressure space is connected with said low pressure space,
a return passage (15) interconnecting said small diameter portion of said
stepped diameter bore with said low-pressure space (13);
a spring operatively interposed between said control valve bushing (17) and
control valve body (22) resiliently biasing the latter to its closed
position wherein said seat engages said sealing surface;
an injection valve (49) operable to inject fuel into an engine cylinder;
a continuously open high-pressure fuel line (48) extending between and
interconnecting said high pressure hole (12) with said injection valve
(49), said high pressure hole (12) and said high pressure fuel line (48)
forming a continuously open flow connection between said high pressure
space (11) and said injection valve (49);
a liquid-filled damping space (33) at one axial end of said control valve
bushing (17);
an anchor plate (30) secured to an axial end of said control valve body
(22) and disposed within said damping space (33);
a choke hole (37) connecting said damping space (33) in free flow
communication with said return passage (15);
a venting line (39) connected to the highest point of said damping space
(33);
a pressurizing valve (40) connected to said venting line (39) having a
relief pressure less than the pressure in said low-pressure space (13);
and
an electromagnetic actuating device operatively associated with said
control valve body and selectively operative upon actuation to move said
valve body to its open position in opposition to said spring;
said anchor plate and damping space, valve body, valve bushing, spring and
choke hole being proportioned and arranged to effect a recoilless seating
of said valve body seat on said sealing surface.
3. A fuel injection device for diesel engines, comprising:
a fuel injection pump having
a one piece plunger bushing (5) including
a plunger bore with a first end which is open for receiving a plunger and a
second end,
a high pressure hole (12) in said plunger bushing (5) connected to said
second end of said bore, said second end of said bore being closed except
for said high pressure hole (12),
a high pressure space (11) at said second end of said plunger bore,
a low pressure space connected to said plunger bore at a substantial
distance from said second end,
a stepped diameter bore having a large diameter portion and a small
diameter portion, said stepped diameter bore extending transverse to and
intersecting said high pressure hole closely adjacent to said high
pressure space, and
a return passage (15) interconnecting said small diameter portion of said
stepped diameter bore with said low-pressure space,
a pump plunger (4) reciprocatably mounted in said plunger bore,
a seat valve including
a control valve bushing (17) having stepped diameter exterior surfaces
having a complementary fit with said stepped diameter bore in said plunger
bushing, a stepped diameter interior bore having a large diameter portion
and a small diameter portion with a seating surface therebetween and a
high-pressure control hole (28) extending radially through said valve
bushing in alignment with said high pressure hole (12),
a stepped diameter cylindrical control valve body having a large diameter
portion, a small diameter portion and a control valve seat formed between
said large and small diameter portions, said large and small diameter
portions being in axial sliding engagement with said stepped diameter
interior bore of said control valve bushing, said control valve body being
axially shiftable between a closed position in which said control valve
seat sealingly engages said seating surface thereby preventing flow from
said high-pressure hole (28) to said low-pressure space via said return
passage and an open position in which flow from said high pressure hole to
said low-pressure space is permitted,
a spring operatively interposed between said control valve bushing and said
control valve body resiliently biasing said control valve body axially
toward its closed position,
a liquid-filled damping space (33) in said control valve bushing and
an anchor plate (30) secured to one of the axially opposite ends of said
control valve body, said anchor plate (30) being operatively positioned in
said damping space (33),
seal elements (20) operable to seal said control valve bushing (17) in
relation to said stepped diameter bore at opposite sides of said
high-pressure control hole (28),
an electromagnetic actuating device operatively associated with said
control valve body and selectively operative upon actuation to move said
body to its open position in opposition to said spring,
a fuel supply passage connected to said low-pressure space,
a check valve in said fuel supply passage operable only to admit fuel to
said low-pressure space,
a pressure relief valve connected to said low-pressure space operable to
regulate the maximum fuel pressure in said low-pressure space,
an injection valve (49) operable to inject fuel into an engine cylinder,
and
a continuously open high-pressure fuel line (48) extending between and
interconnecting said high pressure hole (12) with said injection valve
(49), said high pressure hole (12) and said high pressure fuel line (48)
forming a continuously open flow connection of substantially uniform flow
cross section between said high pressure space (11) and said injection
valve (49).
4. The fuel injection device of claim 3 wherein said seat valve includes a
choke hole (37) connecting said damping space (33) in free flow fuel
communication with said return passage.
5. The fuel injection device of claim 4 and further comprising a venting
line connected to the highest point of said damping space.
6. The fuel injection device of claim 5 and further comprising a
pressurizing valve (40) is connected to said venting line (39), the relief
pressure of said pressurizing valve being less than the pressure in said
low-pressure space (13).
7. The fuel injection device of claim 6 wherein said anchor plate (30) is
of a relatively large mass and predetermined geometry, wherein the moving
parts of said seat valve are of a predetermined mass, said spring
possesses a predetermined force and said fuel has a predetermined
viscosity in operating temperature range of said engine, the force of the
electromagnetic actuating device is a predetermined value and the
clearance between the anchor plate (30) and the electromagnetic actuating
device (7) in the non actuated condition of the latter is a predetermined
distance whereby the contact of the stepped diameter cylindrical component
on said control valve seat (25) is recoilless.
Description
CROSS REFERENCE TO RELATED APPLICATION
Reference is made to a copending patent application Ser. No. 07/447,683
filed Dec. 8, 1989 by Reda Rizk and HansGottfried Michels for a Unit Fuel
Injector disclosing some features shown in this application.
TECHNICAL FIELD
This invention relates to a fuel injection device for diesel engines.
PRIOR ART STATEMENT
Fuel injection pumps of this design type can draw in fuel via a suction
hole in the plunger bushing and/or via a suction valve located in the
region of the delivery space.
In another design type of fuel injection pumps, the fuel is drawn in via a
seat valve arranged in the region of the high-pressure space and actuated
by means of an electromagnetic adjusting device.
In both design types, after drawing in, the fuel is delivered by the pump
plunger into the injection line via a delivery or relief valve.
The delivery or relief valve has the purpose of lowering the pressure in
the injection line to a certain degree after the termination of the
injection process and preventing the injection line from being sucked
empty on the next drawing in of fuel. Both rapid closing of the injection
valve with no after-injection and cavitation-free operation of the
injection system are to be effected by this means.
British patent application publication GB 2079382 shows a sliding spool
valve for controlling flow of low pressure fuel to the pump pressure
chamber and for connecting the high pressure delivery passage to the low
pressure fuel source to terminate injection.
OBJECTS AND BRIEF SUMMARY OF THE INVENTION
It is the object of the invention to improve fuel injection and thus
combustion in diesel engines. Furthermore, the maintenance expense is to
be kept low and the dimensions and costs kept small by means of the simple
design of the fuel injection device.
The inventors have made a surprising discovery. Namely, that a delivery or
relief valve can be dispensed with if a continuous flow connection exists
between the high-pressure space and the low-pressure space in the time
interval between the end of delivery and the onset of delivery. Thus, the
pressure in the high-pressure region is relieved into the low-pressure
space without any need for a delivery or relief valve. Since the
high-pressure region is at the pressure of the low-pressure space in the
time interval between the end of delivery and the onset of delivery, void
formation in the high-pressure region due to the downward motion of the
pump plunger is positively prevented. Due to the absence of the delivery
or relief valve, the dead space is substantially reduced, since now a
constant or roughly constant flow cross section can be realized between
the delivery space and the injection valve. In this manner, the rigidity
of the high-pressure system is enhanced so that, for equal delivery rates
of the injection pump, higher injection pressures can be attained. Higher
injection pressures, moreover, lead to improved combustion with low fuel
consumption and low pollutant emission.
Additionally, the elimination of the delivery valve provides a
simplification and cost reduction of the injection unit. Furthermore, the
useful life and the expense of maintaining the injection device are
reduced by means of the elimination of a part subject to wear.
By means of the use of a seat valve with an electromagnetic adjusting
device as a control element in accordance with the invention, and on the
basis of the short response time of said control element, a more rapid
pressure relief of the high-pressure region is achieved than in the usual
mechanical control-edge system, especially as the pressure-relief volume
is substantially reduced by means of the elimination of the relief valve.
Because the switching time of the electromagnetic actuating device is
constant over time and independent of speed, this advantage manifests
itself particularly at low motor speeds.
By means of the position and arrangement of the seat valve in accordance
with the invention, the dead space is likewise kept small since, despite
the electromagnetically actuated seat valve built into the flow
connection, said flow connection between the high-pressure space and the
injection valve exhibits a virtually constant flow cross section. This is
made possible because an annular high-pressure space is also provided, as
a bypass line with constant flow cross section, in the region of the
electromagnetically actuated seat valve.
In the approach in accordance with the invention, the high-pressure region
is pressurized, during drawing in, with the inlet pressure prevailing in
the low-pressure space. This so-called steady pressure, the level of which
is guaranteed in accordance with the invention by a pressurizing valve in
the suction space, insures in an advantageous fashion the stability of the
onset of delivery and the quantity delivered by the injection pump and
reduces the cavitation danger in the system.
The approach in accordance with the invention offers, in a further
development, the advantage that the arrangement of the injection elements
can be optimally adapted to the design peculiarities of the motor housing
in each case.
By means of an advantageous development of the invention, the fuel
injection pump is prevented from running dry with the motor stopped since,
in accordance with the invention, a tightly closing supply valve closes
off the low-pressure space from the fuel supply.
The approach in accordance with the invention offers, in a further
development, the advantage that the arrangement of the injection pump
elements can be optimally adapted to the design peculiarities of the motor
housing in each case.
By means of an advantageous development of the invention, the injection
line becomes especially short and thus the dead space especially small so
that the injection pressure can become especially high.
By means of an advantageous development of the invention, separate
fabrication and testing and individual replacement of the injection pump
element and the control valve or the electromagnetic actuating device are
made possible.
By means of an advantageous development of the invention, a reduction in
the dead space of the fuel injection device is achieved.
For unrestricted exchangeability of the control valve, it is important to
provide some clearance between the stepped hole in the injection pump
element and the control valve.
The assembly clearance is bridged over in an advantageous fashion by means
of two seal elements which, besides their high-pressure sealing function,
provide a support for the control valve in the stepped hole of the plunger
bushing.
By means of this invention, the high-pressure fuel, when it is spilled by
the control valve body, is led through a hole in the plunger bushing back
to the low-pressure space. Expensive external connecting lines with their
danger of leakage are thus avoided.
A further advantageous development of the invention is the arrangement,
parallel to the axis of the control valve body, of the elements with which
the control valve is fastened to the plunger bushing. This arrangement
prevents distortion and thus seizing of the control valve body in the
control valve bushing.
By means of a spill groove in the pump plunger, the delivery of the
injection pump is interrupted, independently of the operability of the
control valve, before the delivery runs into the dome radius of the
injection pump cam.
By means of the arrangement of the anchor plate in a vented and fuel-filled
space in accordance with the invention, recoilless closing and thus exact
control of the beginning of fuel delivery and quantity of fuel delivery is
achieved, provided the clearance between the anchor in its picked-up state
and the electromagnetic actuating device is adapted to the various design
parameters of the control valve.
An advantageous development of the invention, namely a longitudinal and
transverse leakage oil hole in the control valve body, avoids a separate
leakage oil return line, the expense associated therewith, and the danger
of leakage.
By means of the embodiment of the exterior outline of the injection pump
element in accordance with the invention, replacement of a standard
element by the injection pump element with control valve is possible
without any reworking.
The position of the high-pressure space and the suction or spill hole in
accordance with the invention makes possible a minimal dead space in the
high-pressure region, which is comparable with the dead space of a
standard element.
BRIEF DESCRIPTION OF THE DRAWINGS
Other features of the invention are derived from the description that
follows and from the drawings, in which exemplary embodiments of the
invention are illustrated schematically.
FIG. 1 shows a transverse section through a schematically illustrated
injection pump with electromagnetically actuated control valve.
FIG. 2 shows a transverse section through the fuel injection device.
FIG. 3 shows a detailed section through the fuel injection device.
DETAILED DESCRIPTION OF THE DRAWINGS
The fuel injection device consists of an injection pump element 1 and a
control valve 2, the injection pump element 1 simultaneously being the
carrier of the control valve 2. The injection pump element is assembled
from a pump plunger 4 and a plunger bushing 5 and the control valve 2 from
a seat valve 3 and an electromagnetic actuating device 7.
The pump plunger 4, which is sealingly guided in a bore of a plunger
bushing 5, forms together therewith a high-pressure space 11 at the upper
closed end of the bore. The pump plunger 4 has a spill groove 8, which is
connected to a high-pressure space 11 via a longitudinal spill hole 9 and
a transverse spill hole 10. When the plunger 4 is located at bottom dead
center, the high-pressure space 11 is connected to the low-pressure space
13 via a suction or spill hole 14. The low-pressure space 13 is
pressurized by a fuel delivery pump, not illustrated, via a supply line
51. The pressure in the low-pressure space 13 is held constant by a
pressurizing valve 52.
The plunger 4 is moved axially against the force of a compression spring 53
by a cam 55 via a roller shaft 54. By this means, the fuel is delivered
into a high-pressure hole 12 after the closing of the suction or spill
hole 14. As long as the seat valve 3 is open, the delivered fuel flows
back into the low-pressure space 13 via the annular high-pressure space
26, the control valve seat 25, the annular low-pressure space 27 and the
return hole 15.
As soon as the seat valve 3 is closed by means of excitation (actuation) of
the electromagnetic actuating device 7, high-pressure delivery begins,
fuel being delivered to the injection valve 49 by means of the
high-pressure hole 12, the annular high-pressure space 26 and the
injection line 48.
The high-pressure space 11, the high-pressure hole 12 with annular
high-pressure space 26, the injection line 48 and the injection valve 49
together form a high-pressure region 50.
High-pressure delivery is ended by means of opening of the seat valve 3.
The connection thereby created to the low-pressure space 13 effects a
pressure relief of the high-pressure region 50, which is at the pressure
of the low-pressure space 13 until the closing again of the seat valve 3.
By this means, void formation during the downward motion of the pump
plunger is prevented and constant pressure conditions at the beginning of
the next injection are insured, which constant pressure conditions lead to
stable onset of delivery and quantitative characteristics.
The supply valve 51 and the pressurizing valve 52, which are made as
especially tightly closing valves, prevent the low-pressure space 13 and
the high-pressure region 50 from running dry with the motor stopped, by
which means difficulties in the starting of the motor are avoided.
The high-pressure space 11 is carried up to a short distance below a
stepped hole 19, which serves to accommodate the control valve 2. By this
means, the dead space in the high-pressure space 11 is minimized, which
proves especially advantageous at high injection pressures.
The high-pressure space 11 has no cover plate because the injection pump
element 1 is embodied as a so-called "monoelement." The embodiment as a
monoelement advantageously increases the high-pressure capability of the
fuel injection device by minimizing the pressure space expansion.
In the plunger bushing 5 there is a suction or spill hole 14, which
connects the high-pressure space 11 to a low-pressure space 13, which in
turn is connected to the suction space, not illustrated, of the injection
pump housing.
The suction or spill hole 14 is drilled from the low-pressure space 13
obliquely in the direction of the high-pressure space 11 in order to allow
for the position of the high-pressure space 11.
The low-pressure space 13 is, furthermore, connected to an annular space 16
in a control valve bushing 17 of the seat valve 3 via a return hole 15. By
this means, an external return line, with attendant construction expense
and a leakage risk, in avoided.
The seat valve 3 sits with a clearance fit in the stepped hole 19 of the
plunger bushing 5 and is supported in two high-pressure sealing elements
20. It is held in a firm connection with the plunger bushing 5 by means of
screws, not illustrated, which are inserted through holes in a cover plate
21 and the plunger bushing 5 and screwed into the control valve bushing
17, without the seat valve 3 being distorted. Furthermore, distortion and
consequently seizing of the seat valve 3 caused by the tightening of the
injection line 48 is avoided by means of the assembly clearance between
the control valve bushing 17 and the stepped hole 19.
A particular advantage of this arrangement consists in that independent
replacement of control valve 2 and injection pump element 1, as well as
the electromagnetic adjusting device 7, is assured. Low-cost fabrication
and repair of the fuel injection device is possible by virtue of this
modular construction.
The seat valve 3 has a control valve bushing 17 and a control valve body
22, which is axially movably guided in the control valve bushing 17,
specifically in a high-pressure guide 23 and a low-pressure guide 24.
With a control valve seat 25, the control valve body 22 separates a
high-pressure annular space 26 from a low-pressure annular space 27. The
high-pressure annular space 26 is connected to the high-pressure space 11
via a high-pressure control hole 28 and the high-pressure hole 12. The
low-pressure annular space 27 is connected to the low-pressure space 13
via the spill hole 29, the annular space 16 and the return hole 15.
The control valve body 22 has a longitudinal leakage oil hole 42 and a
transverse leakage oil hole 43, which create a connection between a
leakage oil space 44 and a spring space 34.
At the end of the control valve body 22 where the low-pressure guide 24 is
located, there is attached an anchor plate 30, which is moved by the
electromagnetic actuating device 7. The attachment of the anchor plate 30
is accomplished by means of a countersunk screw 31 screwed into the
control valve body 22, which screw clamps the anchor plate 30 and a stop
ring 32 axially against the control valve body 22.
The anchor plate 30 is located in a fuel-filled damping space 33, which is
delimited by an intermediate piece 41 and the electromagnetic actuating
device 7. The volume of the damping space 33 is sized such that, upon the
axial movement of the anchor plate 30, no marked flow resistances occur
between the anchor plate 30 and the walls of the intermediate piece 41.
The damping space 33 is connected to a spring space 34, likewise
fuel-filled. In the spring space 34 there is a spring 36, whose force
presses the stop ring 32 in the direction of the stop 35. The stop 35
serves to limit the stroke of the control valve body 22.
The damping space 33 and the spring space 34 are connected to the spill
hole 29 via a choke hole 37.
In the region of the highest point of the damping space 33 in the installed
position, there is made a tapped hole 38 to which a venting or fuel return
line 39 is connected, which line leads to the fuel tank, not illustrated.
Arranged in this venting or fuel return line 39 is a pressurizing valve 40,
whose spill pressure is lower than the delivery pressure of the fuel pump,
not illustrated.
The electromagnetic actuating device 7 with the intermediate piece 41 is
clamped against the control valve bushing 17 by means of screws, not
illustrated, which act parallel to the axis of the control valve body 22,
without distorting said control valve bushing.
The entire low-pressure region of the control valve 2 is sealed off by
means of O-rings 45.
The fuel injection device functions in the following manner:
Upon the delivery stroke, the pump plunger 4 is moved from its bottom dead
center position in the direction of the control valve 2. After running
through a pre-stroke, it first closes the suction and spill hole 14.
Afterward, the plunger 4 delivers fuel into the high-pressure hole 12 and
into the high-pressure control hole 28.
As long as the control valve body 22 with the stop ring 32 and the anchor
plate 30 is held against the stop 35 by the spring 36, the high-pressure
annular space 26 and the low-pressure annular space 27 are connected via
the control valve seat 25. Thereby the fuel delivered flows via the spill
holes 29, the annular space 16 and the return hole 15 back into the
low-pressure space 13.
As soon as the electromagnetic actuating device 7 is excited by a current
pulse, the anchor plate 30 picked up, thereby pulling the control valve
body 22 against the control valve seat nozzle 49 via the injection line
48.
Simultaneously with the picking up of the anchor plate 30, the spring 36 is
prestressed. As soon as the electromagnetic actuating device 7 ceases to
carry a current, the spring 36 lifts the control valve body 22 off its
seat 25. Thus, the fuel again flows into the low-pressure spaces, and fuel
injection is terminated.
A precondition for the precise functioning of the seat valve 3 and thus for
reproducible onset of delivery and invariant quantity delivered, is the
recoilless contact of the control valve body 22 on the control valve seat
25. This is achieved in accordance with the invention by means of a finely
tuned damping of the movement of the control valve body 22. The
displacement flow between the anchor plate 30 and the electromagnetic
actuating device 7 is utilized for damping. The anchor plate is made with
no open axial holes in order to bring about the most effective possible
restricted flow between the anchor plate 30 and the electromagnetic
actuating device 7 at the stroke end.
The requisite degree of damping depends on, among other factors, the moving
mass, i.e., the mass of the control valve body 22 plus anchor plate 30
plus countersunk screw 31 plus stop ring 32 plus a portion of the mass of
the spring 36. Another factor relevant to damping is the spring stiffness
of the control valve seat 25.
The damping itself depends on, among other factors, the fuel viscosity, the
geometry of the anchor plate 30 and the minimum spacing 46 between the
anchor place 30 and the electromagnetic actuating device 7, as well as on
the pressure in the damping space 33. These independent variables must be
adapted to one another. The optimal adaptation is achieved when the
contact of the control valve body 22 on the control valve seat 25 takes
place without any recoil and the prolongation of the movement of the
control valve body 22 due to damping is minimized.
The provision of the damping space 33 with damping liquid, for example
damping oil, can be accomplished via a separate damping oil circuit. In
the present case, in accordance with the invention, fuel is withdrawn from
the low-pressure region, especially from the spill hole 29 of the seat
valve 3, via the choke hole 37. The latter prevents pressure shocks in the
spill hole 29 from reaching the damping space 33.
For proper functioning of the damping, it is important that there is no air
in the damping space 33, since the viscosity and compressibility of the
damping medium are influenced by such air. Furthermore, it is important
that the damping liquid is continuously renewed, since said liquid becomes
heated and ages.
In accordance with the invention, the venting of the damping space 33 is
effected via the tapped hole 38, which is made in such a fashion that it
is located in the region of the highest point of the damping space 33 in
the installed position of the control valve 2.
Connected to the tapped hole 38 is the venting or fuel return line 39, by
means of which the fuel flows via the pressurizing valve 40 back to the
fuel tank, not illustrated. The pressurizing valve 40 insures a certain
liquid pressure in the damping space 33, which pressure is lower than the
maximum delivery pressure of the low-pressure pump, not illustrated, and
is lower than the pressure in the low-pressure spaces of the fuel
injection device. By this means, flow through the damping space 33 and
thus renewal of the damping medium fuel and cooling of the control valve 2
is insured. In addition, the pressurizing valve 40 insures that the
damping space 33 cannot run dry with the motor stopped, which leads to
undamped stroke motion and thus to seat recoil of the control valve 3.
This would result in, among other things, incorrect commencement of
delivery upon restarting of the motor.
The leakage oil from the leakage oil space 44 is led, via the longitudinal
leakage oil hole 42 and the transverse leakage oil hole 43 in the control
valve body 22, to the spring space 34 and thus into the damping oil
circuit. This approach in accordance with the invention saves a separate
leakage oil return line.
For the case of a failure of the control valve 2, the spill groove 8 of the
pump plunger 4 allows spilling of fuel into the suction or spill hole 14
at the end of the delivery stroke. Thus, fuel injection is terminated in
every case before the delivery reaches the dome region of the injection
pump cam and overloads it.
The pump plunger 4 of the injection pump element 1 is substantially easier
to fabricate than a plunger of a standard fuel injection device having a
rotatable spill control device with spill edges cooperating with plunger
spill edges since the rotation device and the precise control edges become
necessary.
The fuel injection device in accordance with the invention allows an exact
determination of the onset of delivery and metering of the quantity of
injected fuel by means of the recoilless contact of the control valve body
22 on the control valve seat 25. Furthermore, it is easy to fabricate and
service, since the principal components, injection pump element 1, control
valve 2 and electromagnetic adjusting device 7, can be fabricated, tested
and replaced individually and independently of one another.
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